Smooth bore, chordal transit-time ultrasonic flow meter that eliminates dependence of meter factor on Reynolds Number

ABSTRACT

An apparatus for determining fluid flow in a pipe including a transit time chordal ultrasonic meter that eliminates dependence of meter factor on Reynolds number for measuring the flow through the pipe. The meter having a bore through which the fluid flows and a plurality of cavities with transducers disposed in the cavities which produce ultrasonic pulses that pass through the fluid and define multiple chords. The fluid velocity measured by clocking the pulses&#39; time traveling diagonally upstream and downstream between pairs of the transducers. The transducers in the cavities isolated from the fluid flow in the bore by each cavity of the cavities having a liner which separates each cavity from the bore. A method.

CROSS-REFERENCE TO RELATED APPLICATIONS

This is a continuation of U.S. patent application Ser. No. 13/718,825filed on Dec. 18, 2012, now U.S. Pat. No. 9,140,593, which is acontinuation of U.S. patent application Ser. No. 12/736,373 filed onOct. 1, 2010, which is a 371 of international applicationPCT/US2009/002094 filed Apr. 3, 2009, which is an internationalapplication of U.S. provisional application Ser. No. 61/125,015 filedApr. 22, 2008, all of which are incorporated by reference herein.

FIELD OF THE INVENTION

The present invention is related to analyzing fluid flow in a pipe usingan ultrasonic flowmeter having a plurality of transducers and a flowelement having a completely smooth bore through which the fluid flows.(As used herein, references to the “present invention” or “invention”relate to exemplary embodiments and not necessarily to every embodimentencompassed by the appended claims.) More specifically, the presentinvention is related to analyzing fluid flow in a pipe using anultrasonic flowmeter having a plurality of transducers and a flowelement having a completely smooth bore through which the fluid flowswhere the flow element has cavities that receive transducers of theflowmeter, and a liner that covers openings of the cavities in the bore.

BACKGROUND OF THE INVENTION

This section is intended to introduce the reader to various aspects ofthe art that may be related to various aspects of the present invention.The following discussion is intended to provide information tofacilitate a better understanding of the present invention. Accordingly,it should be understood that statements in the following discussion areto be read in this light, and not as admissions of prior art.

Transit-time chordal ultrasonic meters determine volumetric flow bynumerically integrating fluid velocities measured on two, four or morechordal paths. In larger meters the results of this numericalintegration of measured velocities usually accord closely with theactual volumetric flow—meter factors that account for the differencebetween theoretical and actual flow rates typically will lie within afew tenths of a percent of 1.000.

In meters having smaller internal diameters with larger transducercavities the agreement between the theoretical and actual is not as goodwhen Reynolds Numbers are below about 500,000. Deviations approach 1%,and vary with the Reynolds Number. FIG. 1 illustrates the problem. Itplots meter factor data for a collection of meters ranging in internaldiameter from 4 inches to 10 inches against Reynolds Number. At aReynolds Number of about 500,000, the meter factors are close totheoretical (i.e., 1.000) but as Reynolds Number diminishes from thisfigure, the departure from theory increases to a maximum of about 0.8%at Reynolds Numbers in the 30,000 to 50,000 range.

Experimental data—specifically the response of the chordal velocities tochanges in Reynolds Number—show that the cause of this non-linearresponse of meter factor to changing Reynolds Number has to do with theresponse of the flow field (the fluid velocity profile) to the geometryof the transducer cavities, such as the geometry for a typical 4 pathmeter in FIG. 2. At low to intermediate Reynolds Numbers, components ofthe fluid velocity enter the cavities, projecting onto the acousticpaths in such a way as to cause the fluid velocity seen by a path to behigher than that which would prevail if the cavities did not exist. Theeffect is greatest on chords furthest from the centerline. As can heseen in FIG. 2 the geometry of the downstream cavities for the outerpaths of a 4-path meter would particularly lend itself to such aresponse.

The degree to which this distortion of the flow field occurs depends onReynolds Number, probably because the attachment (or separation) of theboundary layer in the vicinity of the cavities depends on the relativemagnitudes of the local inertial and viscous forces. At any rate, thehigher-than-expected chordal velocities require meter factors less thanthe theoretical (1.000) to correct them, the amount of the correctionvarying with Reynolds Number.

The nonlinear dependence of meter factor on Reynolds Number presents acalibration problem. If such a meter is applied to the accuratemeasurement of the flows of products have differing viscosities or ifthe application covers a wide range of flows, the range of Reynoldsnumber to which that meter will be subjected will be broad and is likelyto include the range in which the meter factor is sensitive to the valueof the Reynolds Number. Accordingly, the meter must be calibrated in afacility that has the capability to vary Reynolds Number over a widerange so as to establish the Meter Factor-Reynolds Number relationshipwith precision. Such facilities are rare; only two are known to exist inthe United States.

Furthermore, the algorithm for the meter itself must include a provisionfor a Reynolds Number correction, and must receive an input from whichit can determine kinematic viscosity (the other components of ReynoldsNumber, internal diameter and fluid velocity, are already available inthe meter). Fluid viscosity is not easy to measure and is usuallyinferred from other variables, such as fluid density or sound velocityand temperature. The accuracy with which these variables are measuredand the accuracy of the empirical relationship between them and thefluid viscosity affects the accuracy of the Reynolds numberdetermination, and therefore the accuracy of the adjustment to the “raw”meter factor.

The dependence of meter factor, in meters of 10 inch internal diameterand smaller, on Reynolds Number thus leads to increased expense (toperform the special calibrations needed to characterize the meterfactor) as well as to reduced accuracy (because of the uncertaintiesassociated with the correction of the meter factor with a ReynoldsNumber inferred from data in the field).

BRIEF SUMMARY OF THE INVENTION

The present invention pertains to the analysis of flowing fluid througha pipe. The analysis is performed with an ultrasonic flowmeter havingtransducers that are disposed in cavities of a flow element. The fluidin the pipe flows through the flow element, during which time theflowmeter analyzes the flowing fluid.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING

In the accompanying drawings, the preferred embodiment of the inventionand preferred methods of practicing the invention are illustrated inwhich:

FIG. 1 is a graph of meter factor linearity for typical prior art 4-pathchordal meters of 10 inch internal diameter and smaller.

FIG. 2 is a prior art configuration of a typical 4-path conventionalultrasonic meter showing the apertures formed by the cavities containingthe transducer housings.

FIG. 3 is a photograph of a “smooth bore” 4-path chordal ultrasonicmeter.

FIGS. 4a and 4b are representations of a liner arrangement for “smoothbore” ultrasonic meter.

FIG. 5 is a representation of the apparatus of the present invention.

FIGS. 6 and 7 show the energy transmission geometry of the outer chordalpath of a 4-path meter.

FIG. 8 is a graph of the recovery time for a 10% step change in productsound velocity for the keep-full system of FIG. 5.

FIG. 9 is a graph of the rate of change of product temperature toproduce a 3 dB reduction in signal strength for keepfull system of FIG.5.

FIG. 10 is a graph of bypass flow vs. product Reynolds Number.

FIG. 11 is a graph of the meter factor linearity of the “smooth bore”4-path chordal meter versus that for 4-path meters having a conventionalcavity configuration.

DETAILED DESCRIPTION OF THE INVENTION

Referring now to the drawings wherein like reference numerals refer tosimilar or identical parts throughout the several views, and morespecifically to FIGS. 4b and 5 thereof, there is shown an apparatus 10for analyzing fluid flow in a pipe 12. The apparatus 10 comprises anultrasonic flowmeter 14 having a plurality of transducer 16. Theapparatus 10 comprises a flow element 18 having a completely smooth bore20 through which the fluid flows, and a plurality of cavities 22, eachof the cavities 22 has one of the plurality of transducer 16 disposed init and which is in communication with the fluid flowing through the bore20.

The present invention pertains to an apparatus 10 for analyzing fluidflow in a pipe 12. The apparatus 10 comprises an ultrasonic flowmeter 14having a plurality of transducer 16. The apparatus 10 comprises a flowelement 18 having a bore 20 with an internal diameter and a surface 24through which fluid flows, a plurality of cavities 22 each of which hasan opening 26 in the surface 24. Each of the cavities 22 has one of theplurality of transducer 16 disposed in its. The apparatus 10 comprises aliner 28 that covers the openings 26 of the cavities 22 which preventsfluid flowing through the bore 20 from entering the cavities 22.

The apparatus 10 can include a keep full system 30 in fluidcommunication with the cavities 22 that fills the cavities 22 with fluidthat also flows through the element 18. The keep full system 30 caninclude an intake scoop 32 disposed in the pipe 12 upstream from theelement 18, and upstream tubing 34 in fluid communication with theintake scoop 32 and the cavities 22 through which flowing fluid in thepipe 12 flows through the cavities 22. The keep full system 30 can alsoinclude an outtake scoop 36 disposed in the pipe 12 downstream from theelements 18, and downstream tubing 38 in fluid communication with theouttake scoop 36 and the cavities 22 through which fluid flowing throughthe cavities 22 is discharged into the pipe 12. The element 18 can havea fluid path 40 extending through the cavities 22 and in fluidcommunication with the upstream tubing 34 and the downstream tubing 38through which fluid flows through the cavities 22. There can beintermediate tubing 42 that connects channels 44 through the cavities22. The flow path can have capped vents with double valve isolation 52.

The liner 28 can include a plurality of strips 46 attached to theelement 18. The liner 28 can be acoustically invisible with respect tothe transducer 16. The liner in one embodiment is made of steel. Thethicknesses of the liner 28 can be between 0.001 inches and 0.010inches. There can be a strainer 48 disposed upstream of the cavities 22.The strainer 48 can include at least two screens 50.

The present invention pertains to a method for analyzing fluid flow in apipe 12. The method comprises the steps of flowing fluid through a flowelement 18 having a completely smooth bore 20, and a plurality ofcavities 22. There is the step of determining the fluid flow withtransducer 16 of an ultrasonic flowmeter 14 disposed in the cavities 22.

The flowing step can include the step of flowing fluid though the smoothbore 20 having a liner 28 that covers the openings 26 of the cavities 22which prevents fluid flowing through the bore 20 from entering thecavities 22. There can be the step of filing the cavities 22 with fluidthat also flows through the element 18. The filing step can include thestep of flowing fluid from the pipe 12 into an intake scoop 32 disposedin the pipe 12 upstream from the element 18, and through upstream tubing34 in fluid communication with the intake scoop 32 and the cavities 22through which flowing fluid in the pipe 12 flows through the cavities22.

The filing step can include the step of flowing fluid from the cavities22 through downstream tubing 38 in fluid communication with the cavities22 and discharging the fluid from the cavities 22 into the pipe 12through an outtake scoop 36 in communication with the downstream tubing38. The filing step can also include the step of flowing fluid along afluid path 40 extending through the cavities 22 and in fluidcommunication with the upstream tubing 34 and the downstream tubing 38through which fluid flows through the cavities 22. There can be the stepof flowing fluid in the pipe 12 through a strainer 48 disposed upstreamof the cavities 22.

In the operation of the invention, the meter factors of conventionalchordal transit-time ultrasonic flow meters can vary with ReynoldsNumber, thereby increasing the uncertainty of their calibrations as wellas the complexity of the calibration process. This invention involves aconfiguration for a transit-time chordal ultrasonic meter thateliminates this dependence of meter factor on Reynolds Number andimproves the maintainability of multi-chord ultrasonic flow meters.

Transit-time flow meters determine fluid velocity by clocking the timesof pulses traveling diagonally upstream and downstream between pairs oftransducer 16. In a conventional chordal flowmeter 14 the transducer 16are located in cavities 22 which intersect the internal diameter of theflow element 18. The geometry of the intersection between the transducercavity and the internal diameter of the flow element 18 is complexbecause the intersection generally occurs at a chord and not on thecenterline. (FIG. 2 shows a typical intersection configuration.) Theopenings 26 resulting from the intersection of the transducer cavities22 and the internal diameter of the flow element 18 act as apertures forthe transmission and reception of the ultrasonic energy. There is adependence of meter factor on Reynolds Number arising solely because ofthe interaction of the flowing fluid with the cavities 22.

The configuration of the invention disclosed herein is shown in thephotograph of FIG. 3, and diagrammed in FIGS. 4a and 4b . Essentially,the invention eliminates the fluid interaction with the cavities 22 byliner 28 the internal diameter of the flow element 18 with a thin metalfoil. The configuration is referred to herein as a “smooth bore” meter,since the flowing fluid experiences no disturbance from the walls of theflow element 18 through which it flows.

The cavities 22 behind the foil are filled with the process liquid usinga “keep-full” system such as that shown in FIG. 5. The process fluid hasthe same nominal physical characteristics and is at the same nominalpressure as the process fluid. Thus the liner 28 covering the cavities22 experiences no significant pressure load and serves only to eliminateinteraction between the flowing process fluid and the fluid in thecavities 22.

FIG. 5 shows the flow element's 18 upstream entrance showing the intakescoop 32. Also is shown the flow element 18 including transducercavities 22 and transducer housings, and the flow element 18 downstreamexit showing the outflow scoop.

In the flowmeter 14 configuration disclosed herein, the ultrasonicenergy must travel, for each acoustic path, from a transmittingtransducer:

-   -   (1) Through the essentially stagnant fluid in the cavity in        front of the transmitting transducer,    -   (2) Through the liner 28 that separates that cavity from the        flowing fluid,    -   (3) Through the flowing fluid itself, thence    -   (4) Through the liner 28 that separates the cavity of the        receiving transducer from the flowing fluid,    -   (5) Through the receiving transducer cavity to the receiving        transducer.

The well known algorithm used by the flowmeter 14 to converttransit-times to fluid velocity requires that the energy reaching thereceiving transducer be sufficient for reliable pulse detection and thatthe acoustic path described above be predictable. The following is thusapplicable.

-   -   (a) The liner 28 should be acoustically invisible. That is, it        should respond to ultrasound as a compliant diaphragm, the        energy transmission unaffected by the properties of the liner 28        material. To meet this requirement, the wavelength of the        acoustic energy in the liner 28 should be much longer than the        liner 28 thickness.    -   (b) The algorithm of chordal flow meters assumes that energy        entering the fluid from a transmitting transducer reaches a        receiving transducer via a straight line connecting the two.        Differences in the acoustic properties of the fluid behind the        liner 28 and the process fluid will cause refraction, and        therefore deflection of the transmitted energy, reducing the        amount of transmitted energy traveling the algorithm path. The        differences in properties should be limited such that the        fraction of the transmitted energy that reaches the receiving        transducer is sufficient for reliable signal detection.    -   (c) One configuration of the disclosed invention employs a        “keep-full” system that uses the velocity head of the process        fluid to drive that fluid through the cavities 22 behind the        liner 28 (The arrangement is shown in FIG. 5). The principal        purpose of this arrangement is assurance that differences        between the cavity fluid properties and the process fluid        properties, if any, meet the requirements of (b) above. However,        the “keep-full” arrangement of FIG. 5 constitutes a fluid path        40 that bypasses the ultrasonic flow measurement (fluid flow        through the cavities 22 is, on average, normal to the acoustic        beam and therefore is not “seen” by the transiting ultrasound).        The amount of flow bypassing the measurement should not        materially affect the accuracy of the flow measurement, under        all operating conditions.

Tests to confirm the efficacy of the disclosed invention employed theconfiguration shown in FIG. 3. This configuration used a 300 seriesstainless steel liner material. The wavelength of the ultrasound λ isgiven by the quotient of the propagation velocity C and the frequency ofthe ultrasound, f.λ=C/f.  (C1)

To determine the maximum liner 28 thickness constraint, the minimum wavelength is required, hence the lowest propagation velocity and thehighest frequency. For the stainless steel liner, the lowest propagationvelocity for the ultrasound is that of a shear stress wave at about125,000 inches/sec (The propagation velocity for a longitudinal stresswave is about 1.8 times greater). The upper end of the frequency ofultrasound used for the measurement of fluid flow is about 2 MHz. Hencethe minimum wave length of ultrasound in the stainless steel liner isλ=125,000/2,000,000=0.0625 inches ( 1/16 inch). Acoustic “transparency”requires that the liner be smaller than ¼ of this figure. Several liner28 thicknesses were tested to determine how much they attenuated thetransmitted wave. It was found that liners ranging in thickness from0.001 inches to 0.010 inches did not significantly attenuate theultrasound. On the other hand, a liner thickness of ⅛ inch (twowavelengths) was found to produce unacceptably high attenuation. For theflow tests of the invention a thickness of 0.005 inches was chosen—thisthickness provided reasonable structural integrity as well as acceptablysmall attenuation.

The refraction of the acoustic wave at the boundary between cavity andprocess fluids is determined by the geometry of the intersection and thesound velocities of the cavity fluid and the process fluid. If akeep-full system, such as that of FIG. 5 is employed, the two soundvelocities will be equal in the steady state, but the time lag betweenproperties of the fluid in the cavities 22 and the properties of theprocess fluid can cause differences to arise. (The time lag occursbecause the fluid velocity through the keep-full system is much lowerthan that through the meter. For the analysis described in subsequentparagraphs, the sound velocity of the cavity fluid C_(CAVITY) wasassumed to follow that of the process C_(FLUID) according to a firstorder differential equation: C_(FLUID)=τd/dt(C_(CAVITY))C_(CAVITY). Hereτ is the time constant of the keep-full system which is approximated byits volume divided by its flow.) Process fluid sound velocity willchange with its temperature which can vary in time. Additionally, in amulti-product pipeline, the sound velocity of a batch can and usuallydoes differ from the batch which preceded it. The keep full system 30must ensure that the sound velocity differences do not disrupt themeter's operation.

The geometry of the refraction boundary is complex (Refer again to FIG.2). For a 4 path chordal meter, the plane containing the four acousticpaths is most limiting, with the outer paths having a more constraininggeometry than the inner paths. An enlarged view of the outer pathgeometry is shown in FIG. 6. The boundary between the cavity fluid andthe process fluid (maintained by the liner 28) defines the angle ofrefraction. The angle of an incident ray in medium 1 relative to anormal to this boundary, θ₁, is related to the angle of the refractedray relative to the same normal, θ₂, by Snell's law. This law statesthat:Sin θ₁ /C ₁=Sin θ₂ /C ₂  (C2)

Here C₁ and C₂ are the sound propagation velocities in the incidentmedium (the cavity fluid) and the refraction medium (the process fluid)respectively. The difference between the incident angle and therefraction angle, ∂θ₂, owing to a difference between the propagationvelocities in the cavity and the process fluid, ∂θ₂, is given by:∂θ₂=tan θ₁ ∂C ₂ /C ₁  (C3)

FIG. 7 shows the incident and refraction angles. In a 6 inch 4 pathmeter with ½ inch diameter transducer 16, the incident θ₁ is about 68°.The allowable difference between the incident and refraction anglesdepends on the transmission beam pattern, shown in FIG. 6. Usually bydesign the angular width of the beam (given by the angle α) is madenarrow, so as to maximize the fraction of the transmitted energy that iscaptured by the receiving transducer. The beam width a is approximatedby:α=λ/d radians  (C4)

Here λ is the wavelength of the ultrasound in the process fluid and

d is the diameter of the cavity

A narrow beam width is less tolerant of small changes in refractionangle because a small change in θ₂ can direct most of the transmittedenergy away from the receiving transducer. For a ½ inch cavity, atypical process fluid sound velocity of 50,000 inches/second and a 2 MHzfrequency for the ultrasound, the beam width a is about 3°. A beamdeflection of about ½ α will bring about a 30% (3 dB) reduction in thereceived signal. Using ½ α and the geometry of FIG. 6 as a conservativebasis for the acceptable difference between cavity sound velocity andprocess fluid sound velocity, a difference of about 500 inches persecond is calculated. This figure is about 1% of the sound velocity fora typical petroleum product and corresponds to about a 5° F. change inthe temperature of that product.

What does this limitation mean in terms of meter performance? FIGS. 8and 9 answer this question. FIG. 8 plots the time to recover thereceived signal to within 3 dB (70%) of the magnitude prevailing priorto a 10% change in product sound velocity. A typical sound velocity fora petroleum product is about 50,000 inches/second. A 10% change (5,000inches/second) is representative of the difference in sound velocitiesbetween say diesel fuel and gasoline. FIG. 8 indicates that, for theReynolds Numbers likely to prevail in a multi-product pipeline (50,000or greater) recovery to within 3 dB will occur in less than 1 minute.

It should be noted that a received signal attenuated by more than 3 dBwill not necessarily cause the meter to malfunction; the meter accuracymay however be less than its design value for the period when the signalstrength is beyond this bound.

FIG. 9 shows the rate of change of product temperature that can beaccommodated by the Keep-Full system of FIG. 5 while maintaining thereceived signal within 3 dB of its nominal value. Product temperaturechanges typically occur because of changes in ambient temperature, whichimpact product temperature in an above-ground pipeline, and which aretypically slow. FIG. 9 shows that the most limiting allowablerates-of-process temperature change occur with low Reynolds Numbers. Inreal applications, low Reynolds Numbers—in the 10,000 to 20,000range—can occur in small pipelines carrying heavy crude. FIG. 9 showsthat temperature changes in the 10° F./hour range will not cause anacceptable loss of signal strength. Typical changes in producttemperature due to day-night temperature changes are well below thisvalue.

FIG. 10 shows the bypass leakage through the Keep-full system of FIG. 5as a function of product Reynolds Number. For all Reynolds Numbers inwhich the invention disclosed herein might be applied (5,000 to 500,000)the bypass leakage is less than 0.03% of the flow passing through themeter. This potential error due to bypass flow can be corrected for ineither the meter or the installation. Furthermore, should specificapplications require more rapid response of cavity fluid sound velocityto changes in process fluid sound velocity, the flow rate of the“keep-full” system could be increased (by increasing the diameter of theflow passages of the system).

For the proof-of-principle tests, the cavities 22 were filled withprocess fluid using a manual procedure of valves and tubing. The cavityfluid was therefore close to the process fluid both in chemicalproperties and temperature probably within 100 or 200 inches/second.Throughout the tests, signal strength remained acceptable.

FIG. 11 shows the dependence of meter factor of the smooth bore 20 meterof FIG. 3 on Reynolds Number. Also shown is the meter factor of atypical conventional chordal meter (where the cavities 22 are exposed tothe process fluid flow). The improvement in linearity is pronounced.While the conventional meter shows a variation in meter factor withReynolds Number approaching 0.8%, the sensitivity of the smooth bore 20meter is less than 0.1%. Moreover, this small sensitivity ispredictable—the theoretical sensitivity of the quadrature numericalintegration to developed profiles in the Reynolds Number range of thefigure is about 0.1% declining. A correction for this small nonlinearity does not require a Reynolds Number measurement; it can beaffected using the chordal velocity measurements of the meter itself,specifically the ratio of the outer chord velocities to the inner chordvelocities.

The liner 28 material should be tough, to resist abrasion, and corrosionresistant, to prevent changes in surface 24 roughness. It should bereadily available in sheets having the thicknesses meeting the wavelength specifications described above—about 0.005 inches for thestainless steel liner used in the testing. Candidate materials are: 300series stainless steel, titanium, and Inconel. It should be noted thatthe dimensional specifications for chordal locations must take accountof the liner's effect on the internal diameter of the meter. It shouldalso be noted that no finish machining is required on the internaldiameter or the transducer bores 20, since the flow field through themeter does not interact with these surfaces 24.

For production meters the liner 28 would be affixed by tabs to the frontflange of the flow element 18 as shown in FIG. 3 and as was done intesting. The seam weld would be made as small as possible and locatedaway from any of the acoustic paths, as shown in FIG. 4b . A rollingprocess (similar to rolling tubes into a tubesheet, but on a much largerscale) would ensure that the gap between the base metal of the flowelement 18 and the liner 28 was minimized. Two circumferential bands ofan epoxy adhesive, resistant to attack from petroleum products andlocated near the leading and trailing edges of the liner 28, providesadditional assurance that the band would remain fixed in position.

The specifications for the design of the keep-full system are discussedabove, specifically:

-   -   a. The flow rate through the keep-full system should refresh the        fluid in the cavities 22 between the transducer housings and the        liner 28 quickly enough to limit the difference between the        sound velocity of the cavity fluid and the sound velocity of the        flowing product under transient conditions. The difference in        the cavity and product sound velocities should not be allowed to        become large enough to prevent the transmitted ultrasonic beam        from “illuminating” the receiving transducer (that is, the        refraction of the beam at the cavity/product interfaces must be        limited to an acceptable value). This requirement sets a minimum        acceptable keep-full flow rate. The most limiting condition to        which this requirement applies will normally occur at the        minimum product flow rate and the maximum product viscosity both        of which will act to reduce keep full flow (by the reducing the        driving head and by increasing the resistance of the keep full        loop, respectively).    -   b. The flow through the keep full system 30 is not measured by        the chordal ultrasonic meter and hence constitutes an error in        its flow measurement. Although the magnitude of the error may be        reduced by an estimate of the keep full flow, the bypass flow        should nevertheless be limited to ensure that the meter complies        with its accuracy specification. This requirement sets a maximum        keep full flow rate. The most limiting condition to which this        requirement applies will normally occur at the maximum product        flow rate and the minimum product viscosity both of which will        act to increase keep full flow (by increasing the driving head        and by reducing the resistance of the keep full loop,        respectively).

FIGS. 8, 9 and 10 illustrate the ability of a specific keep full system30 to comply with these requirements for a range of products, producttemperatures, and product Reynolds Numbers (i.e., flow rates andviscosities). The calculated responses on which the figures are basedare for a 6 inch, 4 chord meter with the keep full system 30 illustratedin FIG. 5 and having the following characteristics:Driving head H provided by scoop+dischargeH=(efficiency){(local velocity head facing upstream)−(local velocityhead facing downstream)H=η[(+½V²/g)−(−½V²/g)]=ηV²/g

-   -   Here η is the efficiency of the scoop/discharge arrangement and        is taken as 0.7, based on experience with Dahl tube flow meters.    -   V is the product velocity near the wall of the flowmeter 14,        taken as ½ of the mean product velocity    -   g is the gravitational constant

The tubing is stainless steel, selected for its ready availability andcorrosion resistance. For the 6 inch meter of the sample case, a ¼ inchtubing diameter (0.21 inch tube ID) was selected. For the lengths andconfiguration required in this meter size, the resistance of the tubing,in combination with the losses for entrance, exit, and bends led to flowrates meeting the criteria of a and b above, over a wide range ofoperating conditions.

It should be emphasized that the tubing size and other design specificsmust be selected as appropriate for each application; larger meters willgenerally require larger tubing sizes.

The width of the inlet and discharge scoops is about 4 tube diameters;its height is about 1 tube diameter. These dimensions lead to arelatively small disturbance to the flow field, yet capture a largefraction of the local velocity head. The distance between the intakescoop 32 and the acoustic paths of the ultrasonic meter is such that thedisturbance to the axial velocity profile created by the scoop will havedisappeared by the time the profile is sensed by the ultrasonic pulses.The flow field distortion created by a small disturbance d protrudingradially into the flow stream will generally disappear 10 to 20 ddownstream. This requirement is met by the system shown in FIG. 5. Thedownstream facing (discharge) scoop must likewise be removed from theflow field sampled by the acoustic paths, though the separation distanceneed not be as great (a distance of ½ D from the acoustic paths where Dis the internal diameter of the flow element 18 is considered adequate.

Other data for the sample keep full system 30 of FIG. 5 on which theperformance quoted herein is based are listed below. Resistance and flowcalculations were performed using the data of “Flow of Fluids throughValve, Fittings and Pipe,” Crane Co. Technical Paper 410, incorporatedby reference herein.

-   -   Length of tubing, upstream of upstream cavity feeder: 2½ meter        diameters (15 inches) maximum. This tubing is run external to        the flow element 18 itself as shown in FIG. 5. The pressure        stresses in the wall of the flow element 18 itself will not        permit this passage to be drilled axially along the flow element        18. However, the 0.25 inch radial penetration connecting the        tubing to the intake scoop 32 does not require reinforcement        (because of its small size relative to the wall thickness).        Reinforcement may be required for this penetration in larger        flow elements 18 with larger tubing.    -   Length of 0.21 inch feeder to four (4) upstream transducer        cavities 22, 1 meter diameter (6 inches). The dimensions of the        “saddle” that contains the four transducer 16 in Caldon's        standard petroleum meter body are such that no reinforcement is        required for this feeder.    -   Length of tubing, connecting upstream cavity feeder to feeder to        four downstream transducer cavities 22, 3 meter diameters (18        inches). Because of the complex path, this connection is made        external to the meter body itself.    -   Length of 0.21 inch feeder to four (4) downstream transducer        cavities 22, 1 meter diameter (6 inches). As with the upstream        header, no reinforcement is required.    -   Length of tubing connecting the discharge of the downstream        feeder to the downstream facing discharge of the keep full        system 30, 2½ meter diameters (15 inches) maximum. As with the        incoming tubing, this tubing is run external to the flow element        18 itself, for the same reasons. Again, no reinforcement is        required for the ¼ inch radial penetration to the discharge.    -   Number of sudden expansions in keep-full circuit: 9.    -   Number of sudden contractions in keep-full circuit: 9.    -   Number of 90° bends in keep-full circuit: 11.

The static pressure within the keep-full system designed as describedabove will, on average, be about equal the static pressure of theproduct in the flow element 18 and will never be more than ½ of avelocity head above the static pressure of the product. This pressuredifference, 1 or 2 psi, is not capable of producing significantdistortion of the liner 28 covering the transducer cavities 22.

It should be noted that the disclosed invention may find applicationwhere there is little or no dependence of meter factor on ReynoldsNumber—that is, in meters larger than 10 inches in internal diameter andat Reynolds Numbers above 500,000. Some process fluids, crude oilsparticularly, contain waxes and other contaminants that can find theirway into the transducer cavities 22. These deposits can attenuate anddistort the received signals. The use of a liner 28 and a “keep-full”system provides a means for preventing such deposits.

Certain modifications to the “keep-full” system of FIG. 5 are necessaryin such applications, however. Specifically, a strainer 48 could beadded to the system at a location downstream of the intake but upstreamof the cavities 22 to prevent the keep-full flow from introducingunwanted deposits inside the liner 28. The strainer 48 mesh would beselected to limit the size of particulate contaminants to an acceptabledimension. In all likelihood, a “duplex” strainer 48 design could beused, allowing keep-full flow to be maintained through one basket whilethe second basket is removed for cleaning, then replaced. Additionally,a design of the “scoop” that serves as an intake to the keep-full systemcould be different from that of FIG. 5. A flush design at a higherpressure location upstream of the flow element 18 would be desirable (todiscourage particulates from collecting and possibly plugging thekeep-full piping).

Although the invention has been described in detail in the foregoingembodiments for the purpose of illustration, it is to be understood thatsuch detail is solely for that purpose and that variations can be madetherein by those skilled in the art without departing from the spiritand scope of the invention except as it may be described by thefollowing claims.

The invention claimed is:
 1. An apparatus for determining fluid flow ina pipe comprising: a transit time chordal ultrasonic meter thateliminates dependence of meter factor on Reynolds number for measuringthe flow through the pipe, the meter having a smooth bore defined by aliner through which the fluid flows so there is no disturbance to thefluid flow by the bore and a plurality of cavities with transducersdisposed in the cavities which produce ultrasonic pulses that passthrough the fluid and define multiple chords, the fluid velocitymeasured by clocking the pulses' time traveling diagonally upstream anddownstream between pairs of the transducers, the transducers in thecavities isolated from the fluid flow in the bore by the liner thatcovers over each cavity of the cavities with the liner separating eachcavity from the bore; wherein the cavities are separate, distinct andapart from the fluid in the pipe, and the cavities experiencing nosignificant pressure load relative to the pipe or the fluid in the pipe,wherein the cavities are filled with cavity fluid having same nominalphysical characteristics and a same nominal pressure as the pipe fluidin the pipe, with no interaction between the pipe fluid in the pipe andthe cavity fluid in the cavity through the fluid.
 2. A method fordetermining fluid flow in a pipe comprising the steps of: flowing fluidthrough a smooth bore of a transit time chordal ultrasonic meter, thetransit time chordal ultrasonic meter eliminates dependence of meterfactor on Reynolds number for measuring the flow through the pipe, thesmooth bore defined by a liner through which the fluid flows so there isno disturbance to the fluid flow by the bore and a plurality of cavitieswith transducers disposed in the cavities, which produce, with a transittime chordal ultrasonic meter that eliminates dependence of meter factoron Reynolds number for measuring the flow through the pipe ultrasonicpulses that pass through the fluid and define multiple chords, the meterhaving a plurality of cavities with transducers disposed in thecavities, the transducers in the cavities isolated from the fluid flowin the bore by the liner that covers over each cavity of the cavitieswith the liner separating each cavity from the bore; and measuring thefluid velocity by clocking the pulses' time traveling diagonallyupstream and downstream between pairs of the transducers.